JPH0646038B2 - Axial ring fan - Google Patents
Axial ring fanInfo
- Publication number
- JPH0646038B2 JPH0646038B2 JP2507711A JP50771190A JPH0646038B2 JP H0646038 B2 JPH0646038 B2 JP H0646038B2 JP 2507711 A JP2507711 A JP 2507711A JP 50771190 A JP50771190 A JP 50771190A JP H0646038 B2 JPH0646038 B2 JP H0646038B2
- Authority
- JP
- Japan
- Prior art keywords
- dimensionless radius
- dimensionless
- pitch ratio
- blade
- radius
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
- F04D29/326—Rotors specially for elastic fluids for axial flow pumps for axial flow fans comprising a rotating shroud
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
- F04D29/386—Skewed blades
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】 背景技術及び本発明の概要 本発明は、軸流リングファンに関し、特にファンの運転
効率を高めかつファンの騒音を減少せしめることのでき
る軸流リングファンに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an axial flow ring fan, and more particularly, to an axial flow ring fan capable of increasing fan operating efficiency and reducing fan noise.
公知の軸流リングファンの例が、米国特許第4,35
8,245号及び第4,569,632号明細書に開示
されている。前者の特許明細書には、羽根が前方に湾曲
しているファンが示されている。通常の形式では、ハ
ブ、羽根及びリングが一体構造となるように、これらの
ファンは射出成形されたプラスチックから製作されてい
る。An example of a known axial flow fan is U.S. Pat. No. 4,35.
No. 8,245 and No. 4,569,632. The former patent specification shows a fan whose blades are curved forward. In conventional form, these fans are made from injection molded plastic so that the hub, vanes and rings are a unitary structure.
本発明のファンは前方に曲がった(スキューした)羽根
を有しており、その各々前縁は、外周方向で見た場合幾
分サインカーブの形状を成している。この形状は、羽根
の半径方向の領域に沿う羽根のためのピッチ比の変化に
よって規定されている。更に明確に云えば、平均ピッチ
比に対するピッチ比の比として羽根の無次元半径の函数
として規定されている。その場合の特性は、無次元半径
が0.4と0.495との間ではほぼ一定であり、無次
元半径が0.495と0.55との間では減少し、無次
元半径が0.55と0.675との間ではほぼ一定であ
り、無次元半径が0.675と0.85との間では増加
し、また無次元半径が0.85より大きい場合は減少し
ている。ある特定の無次元半径におけるピッチ比は、無
次元半径の6.28倍であり、該無次元半径は角Qのタ
ンジェント倍であり、該角Qは、特定の無次元半径に沿
った、羽根の前縁と後縁とを結ぶ平面への羽根の横断面
の投影でみて羽根の前縁と後縁との間を延びている第1
の線と、後縁点を貫通して延びかつ前記投影の方向に鉛
直である第2の線とが成す鋭角である。羽根の平均ピッ
チ比は、少くとも実際の平均値に充分近似した、羽根の
無次元半径の数値におけるピッチ比の平均値である。こ
こに開示したファンの場合平均ピッチ比に対するピッチ
比は、無次元半径が0.4と0.495との間では約
1.07、無次元半径が0.55と0.675との間で
は約1.044、また無次元半径が0.85では約1.
105である。The fan of the present invention has forwardly curved (skewed) blades, each leading edge of which has a somewhat sinusoidal shape when viewed in a circumferential direction. This shape is defined by the change in pitch ratio for the vanes along the radial region of the vanes. More specifically, it is defined as a function of the dimensionless radius of the blade as the ratio of the pitch ratio to the average pitch ratio. The characteristics in that case are almost constant between the dimensionless radii of 0.4 and 0.495, decrease between the dimensionless radii of 0.495 and 0.55, and the dimensionless radii of 0. It is almost constant between 55 and 0.675, increases when the dimensionless radius is between 0.675 and 0.85, and decreases when the dimensionless radius is greater than 0.85. The pitch ratio at a particular dimensionless radius is 6.28 times the dimensionless radius, which is the tangent times the angle Q, which is the vane along the particular dimensionless radius. First extending between the leading edge and the trailing edge of the blade as viewed in projection of a cross section of the blade onto a plane connecting the leading edge and the trailing edge of the blade.
Is an acute angle formed by a second line extending through the trailing edge point and being perpendicular to the direction of the projection. The blade average pitch ratio is the average value of the pitch ratio in the numerical value of the dimensionless radius of the blade, which is at least sufficiently close to the actual average value. In the case of the fan disclosed herein, the pitch ratio with respect to the average pitch ratio is about 1.07 when the dimensionless radius is between 0.4 and 0.495 and is about 1.07 when the dimensionless radius is between 0.55 and 0.675. Approximately 1.044 and approximately 1.4 when the dimensionless radius is 0.85.
105.
本発明の原理に基いて製作されたファンにあっては、軸
方向流れの改善、内部運転効率の改善、及びファン騒音
の減少が達成されており、該騒音は、回転騒音成分が著
しく減少して、ファンの音質の改善が実現されている。
次に本発明の特徴を、発明を実施するための現時点で考
えられる最良の形態に基いて製作された有利な実施例を
図示している添付の図面に沿って説明することにする。In the fan manufactured based on the principle of the present invention, the improvement of the axial flow, the improvement of the internal operation efficiency, and the reduction of the fan noise are achieved, and the noise has a remarkably reduced rotational noise component. The sound quality of the fans has been improved.
The features of the present invention will now be described with reference to the accompanying drawings which illustrate advantageous embodiments made in accordance with the best mode presently contemplated for carrying out the invention.
図面の簡単な説明 図1は本発明の原理を具体化したファンの軸方向の正面
図である。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an axial front view of a fan embodying the principles of the present invention.
図2は図1のファンの側面図である。2 is a side view of the fan of FIG.
図3は図1の線3−3に沿った拡大横断面図である。FIG. 3 is an enlarged cross-sectional view taken along line 3-3 of FIG.
図4は、図1の矢印4−4の方向でみた拡大断面図であ
って、羽根ピッチを規定する目的で投影された横断面の
形状を示している。FIG. 4 is an enlarged cross-sectional view as seen in the direction of arrow 4-4 in FIG. 1, showing the shape of the cross-section projected for the purpose of defining the blade pitch.
図5乃至図14は、図1の夫々の横断線5乃至14に沿
って切断された拡大投影横断面図である。5-14 are enlarged projection cross-sectional views taken along respective transverse lines 5-14 of FIG.
図15は夫々の前縁縁部における部分拡大図である。FIG. 15 is a partially enlarged view of each front edge portion.
図16は夫々の後縁縁部における部分拡大図である。FIG. 16 is a partially enlarged view of the trailing edge portion of each.
図17はファンの羽根に含まれている一定の関係を図示
したグラフである。FIG. 17 is a graph illustrating a certain relationship included in the fan blades.
有利な実施例の説明 図1及び図2は、本発明の原理を実現している軸流リン
グファン20の、一般的な構成と配置とを示している。
ファン20は、中心ハブ部22と、外方リング24と、
ハブ部22と外方リング24との間を半径方向に延びて
いる多数の羽根26と、を有している。羽根26は、フ
ァンの回転方向で前方に湾曲している。羽根の前縁は符
号28で、後縁は符号30で示されている。図3の断面
は、各羽根の前縁の典型的な形状を表わしている。図3
でみられるように、この形状は幾分サインカーブの形状
を成しており、該形状は軸方向に押し下げられた領域3
2を有し、該領域32は、軸方向に押し揚げられた領域
34の、半径方向で内方に位置している、図1の軸方向
にみられるような押し下げられた領域32は、破線36
にほぼ等しいゾーンを占有しており、1方半径方向に押
し揚げられた領域34は、破線38にほぼ等しいゾーン
を占有している。その際この破線36及び38は、はっ
きりした移行部を表わしているのではなく、むしろこの
ゾーンは、互いにスムーズに入り混って羽根の残部に移
行していると考えるべきである。DESCRIPTION OF THE PREFERRED EMBODIMENTS FIGS. 1 and 2 show the general construction and arrangement of an axial ring fan 20 embodying the principles of the present invention.
The fan 20 includes a central hub portion 22, an outer ring 24,
And a number of vanes 26 extending radially between the hub portion 22 and the outer ring 24. The blades 26 are curved forward in the rotation direction of the fan. The leading edge of the blade is shown at 28 and the trailing edge is shown at 30. The cross-section of FIG. 3 represents the typical shape of the leading edge of each vane. Figure 3
As can be seen in the figure, this shape is somewhat sinusoidal in shape, which is the axially depressed region 3
2, which is located radially inward of the axially lifted region 34, the depressed region 32 as seen in the axial direction of FIG. 36
, And the unidirectionally swept region 34 occupies a zone approximately equal to dashed line 38. The dashed lines 36 and 38 do not then represent a distinct transition, but rather the zones should be considered to smoothly intermix with each other and transition to the rest of the vane.
図4延至図14に図示の横断面は、異なった半径におけ
る投影横断面である。図4は、照合番号40によって指
定された図4の横断面が、横断面42に対しどのように
投影されるかを示している。ファンの中心からの半径
は、横断面40に沿う異なった点に引かれ、次に横断面
の後縁点を貫通して延びている線44に垂直に投影され
る。横断面42の前縁点と後縁点との間に引かれている
線46は、線44と交差して角Qを規定している。羽根
を貫通しているある特定の横断面のピッチ比は、横断線
14を貫く横断面4によって代表されているように、タ
ンジェントQ倍の横断面の無次元半径の6.28倍であ
る。各羽根は、図17のグラフによって規定されている
特徴を有している。図17は、羽根の無次元半径の函数
として平均ピッチ比に対するピッチ比を示している。無
次元半径が0.4と0.495との間にある場合の平均
ピッチ比に対するピッチ比は、ほぼ1.07である。無
次元半径が0.55と0.675との間にある場合の平
均ピッチ比に対するピッチ比は、ほぼ1.044であ
る。無次元半径が0.85の場合の平均ピッチ比に対す
るピッチ比は、ほぼ1.105である。無次元半径が
0.495と0.55との間にある場合の平均ピッチ比
に対するピッチ比は減少し、無次元半径が0.675と
0.85との間にある場合はこれが増加し、かつ無次元
半径が0.85より大きい場合はこれが減少している。
本発明の原理に基いてファンを実際に製作する際、無次
元半径に対しプラスマイナス0.03の公差が許容され
る。平均ピッチ比は、羽根の多数の無次元半径における
ピッチ比の平均値であり、この値は少くともほぼ充分に
実際の平均ピッチ比に等しい。The cross sections shown in FIGS. 4 to 14 are projected cross sections at different radii. FIG. 4 illustrates how the cross-section of FIG. 4 designated by reference number 40 is projected onto cross-section 42. The radii from the center of the fan are drawn at different points along the cross-section 40 and then projected perpendicularly to a line 44 extending through the trailing edge point of the cross-section. A line 46 drawn between the leading and trailing edges of cross section 42 intersects line 44 and defines angle Q. The pitch ratio of a particular cross section through the vane is 6.28 times the dimensionless radius of the tangent Q times cross section, as represented by cross section 4 through transverse line 14. Each blade has the characteristics defined by the graph of FIG. FIG. 17 shows the pitch ratio with respect to the average pitch ratio as a function of the dimensionless radius of the blade. The pitch ratio to the average pitch ratio when the dimensionless radius is between 0.4 and 0.495 is approximately 1.07. The pitch ratio to the average pitch ratio when the dimensionless radius is between 0.55 and 0.675 is approximately 1.044. The pitch ratio to the average pitch ratio when the dimensionless radius is 0.85 is about 1.105. The pitch ratio to the average pitch ratio decreases when the dimensionless radius lies between 0.495 and 0.55 and increases when the dimensionless radius lies between 0.675 and 0.85, And when the dimensionless radius is larger than 0.85, it is reduced.
When actually manufacturing a fan based on the principles of the present invention, a tolerance of plus or minus 0.03 with respect to the dimensionless radius is allowed. The average pitch ratio is the average value of the pitch ratios over many dimensionless radii of the vanes, which value is at least almost fully equal to the actual average pitch ratio.
Claims (2)
前方に湾曲した複数の羽根を有している軸流リングファ
ンにおいて、各羽根が次のような特性を有している、つ
まり平均ピッチ比に対するピッチ比は、羽根の無次元半
径の函数として、無次元半径が0.4±0.03と0.
495±0.03との間ではほぼ一定であり、無次元半
径が0.495±0.03と0.55±0.03との間
では減少し、無次元半径が0.55±0.03と0.6
75±0.03との間ではほぼ一定であり、無次元半径
が0.675±0.03と0.850±0.03との間
では増加し、かつ無次元半径が0.850±0.03よ
りも大きい場合は減少しており、その際ある特定の無次
元半径におけるピッチ比は、タンジェントQ倍の無次元
半径の6.28倍であり、その場合Qは、特定の無次元
半径に沿った、羽根の前縁と後縁とを結ぶ平面への羽根
の横断面の投影でみて羽根の前縁と後縁との間を延びて
いる第1の線と、後縁点を貫通して延びる第2の線とが
成す鋭角であって、投影部の方向に対し鉛直であり、ま
た羽根の平均ピッチ比は、羽根の多数の無次元半径にお
けるピッチ比の平均値であって、実際の平均値に少くと
もほぼ充分に等しくなっていることを特徴とする軸流リ
ングファン。1. An axial flow fan having a plurality of blades which extend between a central hub portion and an outer ring and are curved forward, each blade having the following characteristics. , That is, the pitch ratio to the average pitch ratio is a function of the dimensionless radius of the blade, and the dimensionless radius is 0.4 ± 0.03 and 0.
495 ± 0.03, it is almost constant, the dimensionless radius decreases between 0.495 ± 0.03 and 0.55 ± 0.03, and the dimensionless radius is 0.55 ± 0. 03 and 0.6
It is almost constant between 75 ± 0.03, the dimensionless radius increases between 0.675 ± 0.03 and 0.850 ± 0.03, and the dimensionless radius is 0.850 ± 0. When it is larger than 0.03, it decreases, and the pitch ratio at a certain dimensionless radius is 6.28 times the dimensionless radius of the tangent Q times, in which case Q is a certain dimensionless radius. Through a trailing edge point and a first line extending between the leading and trailing edges of the blade as seen in projection of the blade's cross-section onto a plane connecting the leading and trailing edges of the blade Is an acute angle formed by a second line extending perpendicularly to the direction of the projection portion, and the average pitch ratio of the blades is an average value of the pitch ratios at a number of dimensionless radii of the blades, An axial-flow ring fan, characterized in that it is at least nearly equal to the actual average value.
半径が0.4±0.03と0.495±0.03との間
ではほぼ1.07であり、また無次元半径が0.55±
0.03と0.675±0.03との間ではほぼ1.0
44であり、また無次元半径が0.850の場合はほぼ
1.105であることを特徴とする、請求項1記載の軸
流リングファン。2. The pitch ratio with respect to the average pitch ratio is approximately 1.07 between the dimensionless radii of 0.4 ± 0.03 and 0.495 ± 0.03, and the dimensionless radius of 0. 55 ±
Approximately 1.0 between 0.03 and 0.675 ± 0.03
44. The axial flow ring fan according to claim 1, wherein the axial flow ring fan has a dimension of 44 and is approximately 1.105 when the dimensionless radius is 0.850.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US07/359,241 US4900229A (en) | 1989-05-30 | 1989-05-30 | Axial flow ring fan |
US359,241 | 1989-05-31 | ||
PCT/EP1990/000856 WO1990015254A1 (en) | 1989-05-30 | 1990-05-29 | Axial flow ring fan |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH04503392A JPH04503392A (en) | 1992-06-18 |
JPH0646038B2 true JPH0646038B2 (en) | 1994-06-15 |
Family
ID=23412961
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2507711A Expired - Lifetime JPH0646038B2 (en) | 1989-05-30 | 1990-05-29 | Axial ring fan |
Country Status (7)
Country | Link |
---|---|
US (1) | US4900229A (en) |
EP (1) | EP0474685B1 (en) |
JP (1) | JPH0646038B2 (en) |
KR (1) | KR920701688A (en) |
CA (1) | CA1324995C (en) |
DE (1) | DE69015184T2 (en) |
WO (1) | WO1990015254A1 (en) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4900229A (en) * | 1989-05-30 | 1990-02-13 | Siemens-Bendix Automotive Electronic Limited | Axial flow ring fan |
US4971520A (en) * | 1989-08-11 | 1990-11-20 | Airflow Research And Manufacturing Corporation | High efficiency fan |
US4995787A (en) * | 1989-09-18 | 1991-02-26 | Torrington Research Company | Axial flow impeller |
DE69228189T2 (en) * | 1991-08-30 | 1999-06-17 | Airflow Res & Mfg | FAN WITH FORWARD CURVED BLADES AND ADAPTED BLADE CURVING AND ADJUSTMENT |
US5489186A (en) * | 1991-08-30 | 1996-02-06 | Airflow Research And Manufacturing Corp. | Housing with recirculation control for use with banded axial-flow fans |
US5273400A (en) * | 1992-02-18 | 1993-12-28 | Carrier Corporation | Axial flow fan and fan orifice |
DE69328212T2 (en) * | 1992-05-15 | 2000-09-07 | Siemens Canada Ltd | Flat axial fan |
US5624234A (en) * | 1994-11-18 | 1997-04-29 | Itt Automotive Electrical Systems, Inc. | Fan blade with curved planform and high-lift airfoil having bulbous leading edge |
US5588804A (en) * | 1994-11-18 | 1996-12-31 | Itt Automotive Electrical Systems, Inc. | High-lift airfoil with bulbous leading edge |
AU2765597A (en) * | 1996-04-22 | 1997-11-12 | Vitara Trading Company Ltd. | Surfaces for movement of media |
US5769607A (en) * | 1997-02-04 | 1998-06-23 | Itt Automotive Electrical Systems, Inc. | High-pumping, high-efficiency fan with forward-swept blades |
CN2304777Y (en) * | 1997-05-28 | 1999-01-20 | 韩玮 | Fan with wheel style paddles |
US5906179A (en) * | 1997-06-27 | 1999-05-25 | Siemens Canada Limited | High efficiency, low solidity, low weight, axial flow fan |
US6082969A (en) * | 1997-12-15 | 2000-07-04 | Caterpillar Inc. | Quiet compact radiator cooling fan |
FR2784422B3 (en) * | 1998-10-12 | 2000-09-22 | Ecia Equip Composants Ind Auto | IMPROVED PROPELLER AND MOTOR-FAN GROUP PROVIDED WITH THIS PROPELLER |
US6599085B2 (en) | 2001-08-31 | 2003-07-29 | Siemens Automotive, Inc. | Low tone axial fan structure |
FR2965315B1 (en) * | 2010-09-29 | 2012-09-14 | Valeo Systemes Thermiques | FAN PROPELLER WITH CALIBRATION ANGLE VARIE |
CN104061185A (en) * | 2013-03-22 | 2014-09-24 | 技嘉科技股份有限公司 | Flow guide fan blade, fan and fan module |
EP3084230A1 (en) * | 2013-12-17 | 2016-10-26 | Dacs A/S | Axial flow fan with blades twisted according to a blade pitch ratio that decreases (quasi) linearly with the radial position |
JP2015155681A (en) | 2014-02-21 | 2015-08-27 | 株式会社デンソー | blower |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1518501A (en) * | 1923-07-24 | 1924-12-09 | Gill Propeller Company Ltd | Screw propeller or the like |
US2684723A (en) * | 1950-09-07 | 1954-07-27 | Guy S Faber | Propeller-type fan blade |
US3416725A (en) * | 1967-10-12 | 1968-12-17 | Acme Engineering And Mfg Corp | Dihedral bladed ventilating fan |
DE2636056C2 (en) * | 1976-08-11 | 1983-07-21 | Rhein-Flugzeugbau GmbH, 4050 Mönchengladbach | Blade for a rotor, in particular a propeller |
JPS6021518Y2 (en) * | 1980-03-07 | 1985-06-26 | アイシン精機株式会社 | Fan for internal combustion engine cooling system |
US4358245A (en) * | 1980-09-18 | 1982-11-09 | Bolt Beranek And Newman Inc. | Low noise fan |
US4569632A (en) * | 1983-11-08 | 1986-02-11 | Airflow Research And Manufacturing Corp. | Back-skewed fan |
US4548548A (en) * | 1984-05-23 | 1985-10-22 | Airflow Research And Manufacturing Corp. | Fan and housing |
US4569631A (en) * | 1984-08-06 | 1986-02-11 | Airflow Research And Manufacturing Corp. | High strength fan |
IT206701Z2 (en) * | 1985-08-02 | 1987-10-01 | Gate Spa | AXIAL FAN PARTICULARLY FOR VEHICLES |
JPS62195494A (en) * | 1986-02-21 | 1987-08-28 | Aisin Seiki Co Ltd | Cooling device for internal combustion engine |
US4900229A (en) * | 1989-05-30 | 1990-02-13 | Siemens-Bendix Automotive Electronic Limited | Axial flow ring fan |
-
1989
- 1989-05-30 US US07/359,241 patent/US4900229A/en not_active Expired - Lifetime
- 1989-08-16 CA CA000608454A patent/CA1324995C/en not_active Expired - Fee Related
-
1990
- 1990-05-29 DE DE69015184T patent/DE69015184T2/en not_active Expired - Fee Related
- 1990-05-29 WO PCT/EP1990/000856 patent/WO1990015254A1/en active IP Right Grant
- 1990-05-29 JP JP2507711A patent/JPH0646038B2/en not_active Expired - Lifetime
- 1990-05-29 EP EP90908230A patent/EP0474685B1/en not_active Expired - Lifetime
-
1991
- 1991-11-27 KR KR1019910701700A patent/KR920701688A/en active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
DE69015184D1 (en) | 1995-01-26 |
JPH04503392A (en) | 1992-06-18 |
DE69015184T2 (en) | 1995-05-18 |
KR920701688A (en) | 1992-08-12 |
US4900229A (en) | 1990-02-13 |
EP0474685A1 (en) | 1992-03-18 |
EP0474685B1 (en) | 1994-12-14 |
CA1324995C (en) | 1993-12-07 |
WO1990015254A1 (en) | 1990-12-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JPH0646038B2 (en) | Axial ring fan | |
EP0475957B1 (en) | Axial flow ring fan with fall off | |
JP4035237B2 (en) | Axial blower | |
JP3204208B2 (en) | Mixed-flow blower impeller | |
EP0992693B1 (en) | Axial fan | |
JPH06159290A (en) | Fan | |
JP2008507652A (en) | Axial impeller with increased flow rate | |
CN210265263U (en) | Fan wheel of axial fan and axial fan | |
US11506220B2 (en) | Fan wheel with three dimensionally curved impeller blades | |
EP0491816B1 (en) | Quiet clutch fan blade | |
WO2009036403A2 (en) | Fan with structural support ring | |
US4995787A (en) | Axial flow impeller | |
US20020114699A1 (en) | Method of assembling a high solidity axial fan | |
JPH10213094A (en) | Impeller for centrifugal compressor | |
JP3082586B2 (en) | Propeller fan | |
JP3473549B2 (en) | Blower impeller and air conditioner equipped with the blower impeller | |
JP2859448B2 (en) | Multi-wing fan | |
JP3831994B2 (en) | Blower impeller | |
CN116249838B (en) | propeller fan | |
JPH04159498A (en) | Impeller of multiblade fan | |
JP3004946U (en) | Centrifugal fan | |
JPH0416000Y2 (en) | ||
JP4766830B2 (en) | Fan for low load heat exchanger | |
JPH04234599A (en) | Axial air impeller | |
JPH0448960B2 (en) |